Traverse control mechanism



July 3, 1962 D. J. LAMB ET AL TRAvERsE CONTROL MECHANISM Filed Aug. 27, 1959 MTTORNEYS United States Patent 3,042,326 TRAVERSE CGNTROL MECHANISM Douglas J. Lamb, Gulf Breeze, and William H. Hills,

Pensacola, Fla., assignors, by mesne assignments, to

Monsanto Chemical Company, a corporation of Delaware Fiied Aug. 27, 1959, Ser. No. 836,401 7 Ciaims. (Cl. 242-263) This invention relates to a traverse control mechanism such as may be used in spinning and twister frames, and particularly to such mechanisms as may be employed in draw-twisting operations for producing a package of yarn on a bobbin.

In a draw-twisting operation yarn packages are pro duced by feeding a continuous iilament through a ring traveler mounted on a reciprocating ring rail onto a rapidly rotating spindle. This operation is, of course, well known in the art. The shape of the package obtained can be regulated within limits by varying the rate of motion of the reciprocating ring rail while the length of the stroke remains the same, by changing the distance of the stroke or by varying the position of the stroke with relation to the length of the bobbin.

ln a preferred embodiment of the present invention, a

fluid actuated traverse control mechanism is provided which produces a constantly diminishing stroke of the reciprocating ring rail so as to produce a package having a uniform barrel portion and tapered upper and lower sections.

ln previously suggested mechanisms for producing a diminishing traverse motion, mechanically operated devices have generally been employed. Several drawbacks have been encountered in using such devices, among which are the inability to obtain suliiciently high traverse speeds and rapid enough reversal of the traverse stroke. Eecause of this latter defect, there is a pause at the top and bottom of each stroke, during which too many wraps of yarn are made .around the bobbin, thus producing a ridge of yarn at each end ofthe barrel.

The present invention provides an apparatus for reciprocating a ring rail by uid means so that the movement of the piston is caused to reverse at the end of its stroke at Aa predetermined but constantly moving point.

It is an object of this invention to overcome the defects of the prior art discussed above.

lt is specifically an object of this invention to provide a traverse control mechanism which accurately and positively causes a reversal of a uid actuated reciprocating ring rail at a predetermined and constantly moving point.

lt is a further object of this invention to provide such a mechanism which operates wholly independent of the reciprocating movement imparted to said rail.

lt is a further object of this invention to provide a traverse control mechanism which employs means including targets in the path of reciprocation `whereby the distance between strokes is varied by changing the distance of said targets relative to one another.

it is further an object of this invention to provide such a device which is simple in operation and inexpensive in structure.

lt is a further object to provide a means for resetting the device of the invention at the end of each operational cycle.

lt is further an object of this invention to provide such a device which will produce a smooth package of yarn which is free of ridges at the reversal point of the traverse stroke.

It is further an object of this invention to provide a iluid actuated draw-twister operation which maintains a constant high speed during the entire operation with an extremely rapid and positive stroke reversal.

3,042,326 Patented July 3, 19h22 ice Further objects and features of this invention will become apparent to those skilled in the art as the disclosure is made in the following detailed description of a preferred embodiment of the invention as illustrated in the accompanying sheet of drawings, in which:

FIGURE 1 is a schematic elevational View of an embodiment of this invention showing hydraulic traverse control mechanism in combination with the ring rail lifter elements;

FIGURE 2 is a sectional view taken on line 2 2 of FIGURE l looking in the direction of the arrows; and

FIGURE 3 is an enlarged fragmentary sectional View of the overload release mechanism of the device shown in FIGURE l.

Referring now to the drawings, reference numeral lil indicates a piston rod slidably engaged in a hydraulic cylinder 12 by a piston 14. Entering at opposite ends of the hydraulic cylinder are feed lines 16 and 18 connected to a four-way snap-action valve indicated by reference numeral 20. Fluid lines 22 and 24 enter the valve 2t! from a pump 26. An oil reservoir 27 and a ow control valve 29 are provided in the uid line 24. A relief valve 31 is situated in line 22. Reference numeral 28 denotes the control lever for the four-way valve.

The end of the piston rod 10 is connected to a roller chain or cable 30 which in turn is attached to a quadrant arm 32. Reference numeral 34 denotes a hexagonal main cross shaft to which the quadrant arm 32 is rigidly attached. A connecting rod arm 36, also rigidly attached to the cross shaft 34, is pivotably connected by a pin 37 to a connecting rod 38, which, in turn, is pivotably connected by a pin 39 to a secondary connecting rod arm 40. This secondary connecting rod .arm 49 is rigidly attached to a hexagonal cross shaft 42, to which is also rigidly attached a lifter arm 44. Connected to the end of the lifter arm is a truck roll 46. Reference numeral 48 denotes a lifter rod which supports a ring rail 50 carrying a ring 52 which surrounds a yarn package 54.

Reference numeral 56 denotes a counter balance spring which is attached to the secondary connecting rod arm 40 at point 57 and to the frame of the machine, which is indicated by reference numeral 58. It will be apparent that the spring 56 exerts a balancing force counter to that imparted by the piston rod 1t) through the roller chain 30 to the conventional lifter elements.

Before going into a description of the traverse control mechanism and other components of the present invention, a brief explanation of the operation of the lifter elements just described will be made for the sake of clarity. The horizontal motion of the piston rod 10 is transmitted through the roller chain 30 to the quadrant arm 32. Since the quadrant arm pivots with the cross shaft 34, it is given an angular motion which, by means of the connecting rod 38l and the secondary connecting rod arm 4t?, imparts a rotary motion to the cross shaft 42. Movement of the piston rod 10 to the right will be seen to eifect a clockwise rotary motion of the cross shaft 42 and thence cause angular movement or" the lifter arm 44 so as to lower the truck roll 46 and allow a downward vertical motion of the lifter rod 4S and the ring rail 59. During the motion of the piston rod 1l)` to the left, the counter balance spring 56 maintains tension in the roller chain 30 and causes an upward angular motion of the lifter arm 44 through the secondary connecting rod arm 40 and the cross shaft 42. Thus, it is seen that the reciprocating horizontal motion of the piston rod 10 is ultimately converted into a reciprocating vertical motion of the lifter rod 48 and the supported ring rail 50.

It should be pointed out that, though the drawing shows only a single secondary shaft cross shaft 42 connected to the main cross shaft 34, in actual operation a plurality of secondary cross shafts are provided `along the length of the draw-twister machine. Attached to each secondary cross shaft are two lifter arms carrying truck rolls which support lifter rods .and attached ring rails. Thus the motion of the piston rod is transmitted through the main cross shaft 34 to a plurality of secondary cross shafts and ring rails simultaneously.

Returning now to the remaining portions of the embodiment illustrated, reference numeral 60 denotes a shipper rod which is attached to the piston rod 10 through a clamp 62 and an overload release mechanism 64. Reference numeral 66 denotes a stop collar secured to the end of the shipper rod 60. The shipper rod passes through and is slidably supported by bearing brackets 68 and 70. Reference numerals 72 and 74 indicate set collars which are mounted on the shipper rod 60. A coil spring 76 surrounding the shipper rod is shown to the right of the set collar 72.

Also supported in the bearing brackets 68 and 70 is a control screw 78 with stop pins 80 and 82, secured at each end thereof. Reference numerals 84 and 86 denote control screw nuts, or targets, threadably mounted on the control screw 78 and having upper portions, or wings thereof, through which passes the shipper rod 60. Fixed at the center of the control screw 78 is a coupling ring 88 which is connected to the control lever 28 for actuation of the four-way valve 20.

The control screw 78 terminates in an Unthreaded portion 90 slidably mounted in a bushing 92 which is connected to and rotatably driven by a sprocket 94. Reference numeral 96 indicates a sprocket chain which connects the sprocket 94 to a sprocket 98 which is driven through a differential gear mechanism 100 by an output shaft 102. Reference numeral 104 indicates a gear reducer which reduces the rotational speed of a drive shaft 106 driven by an electric motor or other means (not shown).

The differential gear mechanisml 100 includes gears 108 and 110 and pinions 112 and 114. The pinions are affixed to a gear cage 116 for rotation about a .vertical axis in the position shown. Rigidly attached to the gear cage 116 is a sprocket 118 connected by a sprocket chain 120 to a sprocket 122 mounted on a shaft 124. The sprocket 118 is rotatably mounted on the shaft 102. Reference numeral 126 denotes a knob and 128 indicates a pin extending from the knob which is insertable into an opening in the sprocket 122 for immobilizing the same. This, in turn, prevents rotation of the sprocket 118. Reference numerals 130 and 132 denote the supports upon which the shaft 124 is mounted, while reference numeral 134 indicates a crank for turning the shaft 124.

Turning now to the operation of the embodiment disclosed, hydraulic fluid is supplied at the required pressure from the reservoir 27 by means of the pump 26 driven by an electric motor or other means (not shown). The fluid is pumped through the conduit 22 and the relief valve 31 to the four-way snap-action valve 20 which is connected by the conduits 16 and 18 to the opposite ends of the hydraulic cylinder 12.

The valve 20, a commercially available article, is actuated by movement `of the control lever 28 to the left or right whereby hydraulic uid will be fed to the right end of cylinder 12 or the left end of the cylinder, depending upon the position of the control lever. Thus, by moving the lever 28 from one position to the other, the tlow of uid is controlled and the piston rod 10 reciprocated.

The flow control val-ve 29 is inserted in the conduit 22 to regulate or meter the amount of fluid being passed through the hydraulic cylinder, so that the reciprocating speed of the piston rod can be altered. It is apparent that by increasing or decreasing the speed of reciprocation, and consequently the speed of traverse of the ring rail, that the shape of the tapered ends of the yarn package is varied.

In the embodiment disclosed the distance of the stroke of the piston rod 10 is continually diminished so as to produce a tapered package 54 by means which will now be A. described. The lshipper rod 68, being attached to the piston rod 10 through the bracket 62 and the overload release mechanism 64, is caused to slide with the piston rod. As the shipper rod 60 slides to the left, for example, the set collar 74 engages target means which comprises the wing Iof the control nut 86 and pushes the control screw 78 upon which control -screw nut 86 is threaded to the left. The coupling ring 88, which is rigidly attached to the center of the control screw and also to lever arm 28, actuates the four-way valve through the lever arm, causing iluid to enter the left side of the cylinder 12. As the shipper rod 60 moves to the right with the piston rod 10, the set collar 72 will engage the wing of the control screw nut 84, thus pushing the control screw 78 and the coupling ring 88 to the right. Hydraulic liuid will then enter the right side of the cylinder 12. It should be pointed out that the spring 76, the function of which will later be described, is small enough in diameter to slide through the opening in the wing of the control screw nut 84 so as to offer no resistance to the movement of the set collar 72 toward the control nut 84.

During the draw-twisting operation, the control screw 78 is continuously rotated by means which include the bushing 92, sprocket 94, chain 96, sprocket 98, differential gear mechanism 100, gear reducer 104, and the drive shaft 186.

Since the control screw has left-handed threads to the left of the coupling ring 88 and right-handed threads to the right of the coupling ring 88, it will be seen that a counter-clockwise rotation of the screw will cause the control screw nuts 84 and 86 to move closer to each other, and thereby reduce the distance of the `stroke of the shipper rod 60 and the piston rod 10.

At the beginning of the dofr" or draw-twisting operation, the control screw nuts 84 and 86 are :screwed up 4against the stop pins and 82 so as to provide a maximum distance between the nuts. The initial length of the piston rod stroke and ring rail traverse is set by locking the collars 72 and 74 the desired distance apart. The closer t0- gether the collars 72 and 74 are placed, the greater the distance they must travel before engaging the nuts 84 and 86, and consequently the greater the length of the piston Istroke will be. The location of the package' on the bobbin, i.e., higher up or lower down on the bobbin, may be regulated by adjustment of the positions of the collars 72 and 74 relative to the end of the shipper rod 60'.

As has been pointed out above, the control screw 78 is continuously rotated in a counter-clockwise direction during the draw-twisting operation. A more detailed description of how this rotational movement is imparted to control screw 78 is as follows:

The output shaft 102, rotating at the desired speed, turns the gear which is mounted thereon in a clockwise direction causing the pinions v112 and 114 to turn the gear 108 in a counter-clockwise direction. The sprocket 98, being mounted on the same shaft which carries the gear 108, will also be rotated in a counterclockwise direction and thence turn the sprocket 94 in a counter-clockwise direction by means of the sprocket 96. This rotation is then imparted through the bushing 92 to the control screw 78, and as the screw rotates in a counter-clockwise direction, the control nuts 84 and 86 move slowly toward the center.

The speed of rotation of the output shaft 102 is, of course, regulated by providing proper gears within the gear reducer box 104. Since the rate of stroke reduction varies directly with the rotational speed of the control screw 78, which is indirectly driven by the output shaft 102, and `since the tapered angle of the yarn package produced depends upon the rate of stroke reduction, it follows that the shape of the package obtained may also be varied by varying the speed of the output shaft 102.

At the end of the doff when the package is completed, the machine is shut down and the control screw must be rotated backwards to bring the control screw nuts 84 and 86 to -their outermost positions ready for the next doif. In order to reset the nuts 84 `and 86 to their outermost positions without requiring an uncoupling of the control screw from its drive, the following operation is oarried out:

The knob 126 is manually pulled back to disengage the pin 128 from the sprocket 122 which it has held locked during the draw-twisting operation described above. While the pin 128 is disengaged, the crank 134 is rotated in a clockwise direction. This imparts `a clockwise motion to the sprocket 122 and also to the sprocket 118 which is bolted to the cage 116. As has been pointed out, the cage 116 carries the pinions 112 and 114. It should be kept in mind that the gear 116 is locked to the output shaft 102 of the gear reducer 104 and is hence immovable. Accordingly, the clockwise rotation of the sprocket 118 causes the clockwise rotation of the cage 116 which is transmitted to a clockwise and faster rotation of the gear 108 through the lpinions 112 and 114. The sprocket 98, mounted to move with the gear 188, is rotated also in a clockwise direction, and this motion is tr-ansmitted through the chain 96 to the sprocket 94 and through the bushing 92 to the control screw 78 to which it is keyed. Since the control screw is equipped with right-hand threads to the right of the coupling ring 88 and left-hand threads to the left of the coupling ring 88, the clockwise rotation of lthis screw causes the control nuts 84 and 86 to move away from each other and back to their original positions against the stop pins 88 and 82. The knob 126 is then released to lock the sprocket 122 and the sprocket 118 in a fixed position, whereupon drive shaft 186 is again actuated to start a new doif cycle.

Another feature of the present invention is the overload release mechanism 64 illustrated in FIGURE 3. This mechanism comprises a housing 135 containing a set screw 136, a spring 138 and a ball 140 situated in a groove 142 in the shipper rod 60.

The overload release mechanism 64 is designed to prevent damage to the traverse control mechanism and the four-way valve 2G which might be caused by the action of the counter balance `spring 56. When the machine is shut down, liquid seeping past the piston allows the counter balance spring '56 to slowly pull the piston rod to one end of its stroke. Eventually, the set collar 74 will hit the left hand control nut 86 and shift the control screw 78 toward the left. Since the pump is not running, the cylinder cannot reverse, and the pull of the counter balance spring S6 will be transmitted through the shipper rod 60 and the control screw 78 to the valve control lever 28.

The overload release mechanism prevents the transmittance of the force of the counter balance spring to the shipper rod 6) by disconnecting this rod from the piston rod when the pulling force thereon exceeds the predetermined lim-it. The ball 148 is spring loaded into the groove 142 at the right end of the shipper rod by means of the spring 138. The amount of spring loading on the ball is adjusted by the set screw 136 so that overload will cause the ball to ride out of the groove 142 and release the shipper rod.

When the machine is started after the overload mechanism has operated, with nuts 84 and 86 being at their end positions against the pins 8h and 82, the piston rod 1t) will travel toward the right carrying the shipper rod 60 with it until the spring 76 passes through the hole in the Wing of the right hand control nut 84 and hits the bearing bracket 68. The movement of the shipper rod is then halted by contact of the right hand set collar 72 against the spring 76, and the housing 135 `slides down the :shipper rod 6U until the ball drops back into its groove 142 and the housing seats up against the stop collar 66. The force of the piston rod moving toward the right then compresses the spring 76 until the right hand set collar 72 hits the right hand control nut 84, shifting the TB valve lever 28 and reversing the travel of the piston rod. The system then continues in normal operation.

In the embodiment above described, a diminishing traverse motion is achieved by utilization of a control screw 78 containing left-handed threads on one side of the screw and right-handed threads on the other side thereof. =It is obvious, however, that by changing the thread arrangement on the control screw, a wide variety of package types can be made. For example, packages with -a conical barrel portion or gently tapered oval shape may be produced as well as the taper top, or bottle shape, -with a straight barrel portion from the bottom of the package to a point about the way up, and a taper from that point to the top of the package. The use of different types of control screws with the apparatus shown is intended to be Within the scope of the disclosure.

It should be understood, of course, that the foregoing disclosure relates to a preferred embodiment of the invention and that numerous modications or alterations may be made therein without departing from the spirit and scope of the invention as set forth in the appended claims.

What is claimed is:

1. In a traverse control mechanism in combination with a ring rail and lifter elements supporting said rail 'for reciprocation thereof, piston means to drive said lifter elements, valve means to reverse the stroke of said piston means, a `rotatably and slidably mounted threaded screw having left-hand threads on one end and right-hand threads on the other end, a stop block threaded on each end of the screw, means attached to said screw to control said valve means, contact means movable with said piston means to strike one of the stop blocks upon each stroke of said piston means so that said screw and said valve control means are caused to slide to actuate said valve means, a gear train connected to the screw for continuously rotating said screw in one direction so that said stop blocks on said screw are moved closer together, and means connected to the gear train for driving said gear train to rotate the screw in the opposite direction.

2. lIn a traversing mechanism having a ring rail and lifter elements supporting said rail for reciprocation, a traverse control comprising a cylinder having a piston connected to the lifter elements for driving said elements, a valve for controlling fluid iiow to the piston and cylinder, a slidably mounted screw having opposite ends threaded oppositely, means attached to the screw Afor actuating the valve when the screw is moved, a rod connected to and movable with the piston, a pair of spaced target members threadedly attached to the screw, a collar attached to the rod for alternately engaging the target members to move the screw and thereby actuate the valve, a differential gear mechanism having a gear cage and an output gear connected to the screw for rotating said screw to vary the spacing of the targets, means for driving the output gear, means for locking the gear cage against rotation as the output gear is driven, and means for rotating the gear cage to reverse the rotation of the screw.

3. In a traverse control mechanism in combination Iwith a ring rail and lifter elements supporting said rail for reciprocation thereof, piston means connected to the lifter elements for driving said elements, valve means to reverse the stroke of said piston means, a rotatably and slidably mounted screw having opposite ends opposi'tely threaded, stop blocks threaded on each end of the screw, means rigidly attached to said screw to control said valve means to reverse the stroke of the piston means, contact means movable with said piston means to strike one of the stop blocks upon `a predetermined amount of movement of said piston means so that said screw and said valve control means are caused to slide to actuate said valve means, and means to continuously rotate said screw so that the relative positions of said stop blocks on said screw is changed to continuously vary said predetermined amount of movement and thereby cause valve actuation to occur at constantly varying stroke positions, said contact means being adjustable relative to the piston means to adjust the initial value of said predetermined amount of movement.

4. In a traverse control mechanism in combination with a ring rail and lifter elements supporting said rail `for reciprocation thereof along a portion of a bobbin, piston means connected to the lifter elements for driving said lifter elements, valve means to reverse the stroke of said piston means, a rotatably and slidably mounted screw having opposite ends oppositely threaded, stop blocks threaded onto each end of the screw, means rigidly attached to said screw to control said valve means, and contact means connected to and movable with said piston means to strike one of the stop blocks upon each stroke of said piston means so that said screw and said valve control means are caused to slide to actuate said valve means, said contact means being adjustable relative to the position of the piston means to shift the portion of the cylinder traversed by the piston means and thereby shift the traversing stroke along the bobbin for changing the conguration of the yarn package wound thereon.

5. In a traverse control mechanism in combination with a ring rail and litter elements supporting said rail for reciprocation thereof, piston means to drive said lifter elements, valve means to reverse the stroke of said piston means, a rotatably and slidably mounted threaded screw having left-hand threads on one end and right-hand threads on the other end, a stop block threaded on each end of the screw, means attached to said screw to control said valve means, a rod adapted to slide parallel to the piston means, an overload release mechanism carried by the piston means and connected to the rod yfor moving said rod with the piston means, contact means mounted on said rod to strike a stop block upon each stroke of said piston means so that said screw and said valve control means slide to actuate said valve means, and means to continuously rotate said screw so that the relative position of said stop blocks on said screw is changed to cause valve actuation to occur at constantly varying stroke positions.

6. In a traversing mechanism having a ring rail and lifter elements supporting said rail for reciprocation, a traverse control comprising -a cylinder having a piston connected to the lifter elements for driving said elements, a valve `for controlling fluid flow to the piston and cylinder, a slidably mounted screw having opposite ends threaded oppositely, means attached to the screw yfor actuating the valve when the screw is moved, a rod, an overload release mechanism carried by the piston and having a spring-loaded element engaging the rod for yieldably connecting the rod to the piston, a pair of spaced target members threadedly `attached to said screw, a collar attached to the rod lfor alternately engaging the target members to move the screw and thereby actuate the valve, a differential gear mechanism having a gear cage and an output gear connected to the screw for rotating said screw to vary the spacing of the targets, means lfor driving the output gear, means for locking the gear cage against rotation as the output gear is driven, and means Afor rotating the gear cage to reverse the rotation of the SCIGW.

7. In a traverse control mechanism in combination with a ring rail and lifter elements supporting said rail for reciprocation thereof, piston means for driving said ili-fter elements, v-alve means for reversing the stroke of said piston means, a rotatably and slidably mounted screw having left-hand threads on one end `and right-hand threads on the other end, a pair of stop Iblocks threaded onto opposite ends of the screw, means attached to the screw for actuating the valve means, a rod mounted for movement parallel to the piston means land having a notch therein, an overload release mechanism carried by the piston means and having a spring-loaded element positioned in the notch in the rod -for yieldably connecting the rod to the piston means, contact means mounted on said rod to strike a stop block upon each stroke of said piston means whereby said screw and said valve actuating means slide to actuate said valve means, and means to continuously rotate said screw so that the relative position of said stop blocks on said screw is changed to cause valve actua-tion to Occur at constantly varying stroke positions.

References Cited in the le of this patent UNITED STATES PATENTS 444,773 Chapin Jan. 13, 1891 1,110,401 Perkins Sept. 15, 1914 2,575,031 Smith Nov. 13, 1951 2,647,698 Woolley Aug. 4, 1953 2,880,661 Kaden et al. Apr. 7, 1959 FOREIGN PATENTS 1,077,807 France May 5, 1954 161,063 Germany June 6, 1905 182,007 Switzerland July 1, 1936 

